高速接触式机械密封动环外侧面人字槽强化换热机理与冷却性能研究

doi:10.11949/0438-1157.20250449

摘要/Abstract

摘要：

为了解决高速工况下接触式机械密封端面过热的问题，提出了一种动环外侧面设有人字槽的接触式机械密封新结构，基于计算流体动力学（CFD）建立了其流固传热数值模型，考察了密封环与密封腔内流场、温度场、压力场和速度场分布，分析了人字槽区与密封腔流体流动传热特性，揭示了对流换热机理与冷却规律。研究结果表明，人字槽结构引发的压差流显著增加了传热表面附近流体与密封腔流体之间的混合效应，提高了人字槽壁面附近流动的湍流强度，该流动减薄了外壁附近的流动和热边界层，增大了局部Nusselt数，强化了换热效果，转速增大时人字槽机械密封的换热性能也随之增强。分析了人字槽角度、槽深、排数以及端面距对换热效果的影响，其中排数与端面距的影响较大。与传统机械密封相比，外侧面人字槽机械密封的端面温升明显下降，转速为10000 r/min时温升下降38.8 K，温度降幅达22.1%，密封温升显著降低，为高性能接触式机械密封的优化设计与工程应用提供了理论依据。

关键词: 接触式机械密封, 外侧面人字槽, 强化换热机理, 热边界层薄化, 冷却性能

Abstract:

To address the issue of overheating in the end faces of contact mechanical seals under high-speed conditions, a novel contact mechanical seal structure with herringbone grooves on the outer side of the rotating ring was proposed. A fluid-solid heat transfer numerical model was established based on computational fluid dynamics (CFD) to examine the distributions of the flow field, temperature field, pressure field, and velocity field within the seal ring and the seal cavity. The heat transfer characteristics of fluid flow in the herringbone groove region and the seal cavity were analyzed, revealing the convective heat transfer mechanism and cooling principles. The results demonstrate that the pressure differential flow induced by the herringbone groove structure significantly enhances the mixing effect between the fluid near the heat transfer surface and the fluid in the seal cavity. Additionally, it increases the turbulence intensity near the groove walls. This flow thins the hydrodynamic and thermal boundary layers near the outer wall, raises the local Nusselt number, and improves heat transfer efficiency. As rotational speed increases, the heat transfer performance of the herringbone-grooved mechanical seal also improves. The influence of herringbone groove angle, depth, number of grooves, and end-face distance on heat transfer was analyzed, with the number of grooves and end-face distance having the most significant impact. Compared with traditional mechanical seals, the end-to-end temperature rise of mechanical seals with herringbone grooves on the outer side was significantly reduced. At a speed of 10000 r/min, the temperature rise decreased by 38.8 K, a 22.1% reduction. This significant reduction in seal temperature rise provides a theoretical basis for the optimized design and engineering application of high-performance contact mechanical seals.

Key words: contact mechanical seal, herringbone grooves on outer side surface, heat transfer enhancing mechanism, thermal boundary layer thinning, cooling performance

中图分类号:

TH 117.2

马学忠, 谢庆祥. 高速接触式机械密封动环外侧面人字槽强化换热机理与冷却性能研究[J]. 化工学报, 2025, 76(10): 5277-5289.

Xuezhong MA, Qingxiang XIE. Research on heat transfer enhancing mechanism and cooling performance of herringbone groove on rotor outer sidewall in high-speed contact mechanical seals[J]. CIESC Journal, 2025, 76(10): 5277-5289.

图/表 24

图1 机械密封结构示意图

Fig.1 Mechanical seal structure

图2 人字槽几何结构示意图

Fig.2 Geometric structure of herringbone groove

表1 几何与工况参数

Table 1 Geometric and operational parameters

参数	数值
端面距l₁/mm	0.1~0.5
槽间距l₂/mm	0.5
槽宽l₃/mm	0.5
动环长度l₄/mm	5.52
静环长度l₅/mm	5.25
槽深h₁/mm	0.1~0.5
进口高度h₂/mm	2
动环内径d₁/mm	28.9
动环外径d₂/mm	32.5
静环外径d₃/mm	34
密封腔外径d₄/mm	42
动环旋转速率n/(r/min)	1800~10000
槽排数n₁	1~4
槽角度α/(°)	10~25

表2 物性参数

Table 2 Physical property parameters

参数名称	C₃H₈O₂(密封介质)	碳石墨(静环)	不锈钢(动环)
k/(W/(m·K))	0.29	18	14
ρ/(kg/m³)	1018.42	1825	7900
c/(J/(kg·K))	3200	419	670
μ/(Pa·s)	0.00705	—	—

表3 摩擦热计算相关参数

Table 3 Related parameters of friction heat

参数	数值
ΔP/MPa	0.8
B/%	75
K/%	50
P_sp/MPa	0.3
f	0.1

图3 边界条件

Fig.3 Boundary conditions

图4 计算域网格划分：(a)装配体网格；(b)人字槽壁面局部网格；(c)边界层局部网格

Fig.4 Computational domain mesh division： (a) assembly mesh; (b) local mesh of herringbone groove wall; (c) local mesh of boundary layer

图5 网格无关性验证

Fig.5 Grid independence verification

图6 模型验证

Fig.6 Model validation

图7 (a) 动静环与密封腔、密封端面的温度场分布； (b) 端面径向温度分布

Fig.7 (a) Temperature field distribution of rotating and stationary rings, sealing chamber and sealing end face; (b) Temperature variation curve along the radius on the end face

图8 人字槽底部的温度与压力分布

Fig.8 Temperature and pressure distribution at the bottom of the herringbone groove

图9 x = 0截面密封腔热边界层

Fig.9 Thermal boundary layer of the sealing chamber at the x = 0 cross-section

图10 (a)密封腔内流场与速度场; (b)密封腔内压力分布

Fig.10 (a) Flow and velocity field in sealing chamber; (b) Pressure distribution in sealing chamber

图11 密封腔不同截面流线与速度分布

Fig.11 Streamline and velocity distributions in sealing chamber at different cross-sections

图12 密封腔 x = 0 截面湍流动能

Fig.12 Turbulent kinetic energy at the x = 0 cross-section of the sealing chamber

图13 (a)外侧表面Nusselt数分布; (b)尾迹流

Fig.13 (a) Nusselt number distribution on outer surface; (b) Wake flow

图14 人字槽角对温度的影响

Fig.14 Effect of herringbone groove angle on temperature

图15 不同槽角下的温度分布

Fig.15 Temperature distribution at different groove angles

图16 槽深对温度的影响

Fig.16 Effect of groove depth on temperature

图17 不同槽深下的温度分布

Fig.17 Temperature distributions at different groove depths

图18 端面距对温度的影响

Fig.18 Effect of end-face distance on temperature characteristics

图19 不同端面距下的温度分布

Fig.19 Temperature distributions at different end-face distances

图20 排数对温度的影响

Fig.20 Effect of row number on temperature

图21 不同排数下的温度分布c —— 比热容，J/(kg·K)d1 —— 动环内径，mmd2 —— 动环外径，mmd3 —— 静环外径，mmd4 —— 密封腔外径，mmEp —— 产热量，Wf —— 摩擦系数h1 —— 槽深，mmh2 —— 进口高度，mmJ —— 热通量，W/m2K —— 压力梯度因子k —— 热导率，W/(m·K)l1 —— 端面距，mml2 —— 槽间距，mml3 —— 槽宽，mml4 —— 动环长度，mml5 —— 静环长度，mmn —— 动环转速，r/minPc —— 接触面压力，MPaPm —— 端面比压Psp —— 弹簧压力，MPaΔP —— 端面两端压差，MPaT —— 环境温度，KTmax —— 温度峰值，KΔT —— 介质温升，Kui,uj —— 速度分量，m/sα —— 槽角，(°)δij —— 克罗内克尔符号λeff —— 有效热导率μ —— 温度T下流体动力黏度，Pa‧sρ —— 介质、动静环密度，kg/m3τij —— 应力张量

Fig.21 Temperature distribution at different row numbers

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